CN101445127A - Variable ratio steering apparatus - Google Patents
Variable ratio steering apparatus Download PDFInfo
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- CN101445127A CN101445127A CNA2008101797307A CN200810179730A CN101445127A CN 101445127 A CN101445127 A CN 101445127A CN A2008101797307 A CNA2008101797307 A CN A2008101797307A CN 200810179730 A CN200810179730 A CN 200810179730A CN 101445127 A CN101445127 A CN 101445127A
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- shaft
- planetary wheel
- mentioned
- steering apparatus
- axle drive
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D6/00—Arrangements for automatically controlling steering depending on driving conditions sensed and responded to, e.g. control circuits
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/008—Changing the transfer ratio between the steering wheel and the steering gear by variable supply of energy, e.g. by using a superposition gear
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
- B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
- B62D1/16—Steering columns
- B62D1/18—Steering columns yieldable or adjustable, e.g. tiltable
- B62D1/19—Steering columns yieldable or adjustable, e.g. tiltable incorporating energy-absorbing arrangements, e.g. by being yieldable or collapsible
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19555—Varying speed ratio
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Power Steering Mechanism (AREA)
- Retarders (AREA)
Abstract
A speed increasing/reducing mechanism is arranged on an opposite portion facing the end of an output shaft and an input shaft, and increases/reduces the rotation speed of the output shaft relative to the rotation speed of the input shaft, when the increasing/reducing mechanism is equipped with a motor in an axial direction, the apparatus will be longer in the axial direction. The input shaft (2) connected with a steering wheel and the output shaft (3) connected with a pinion shaft of a steering mechanism are configured coaxially, the opposite portion is equipped with the speed increasing/reducing mechanism (4) for increasing/reducing the rotation speed of the output shaft (3) relative to the rotation speed of the input shaft (2), and the motor (5) for controlling the speed increasing/reducing mechanism (4) and a locking bracket (16) driven by the motor (5) are arranged on the external side of the speed increasing/reducing mechanism (4) in the radial direction to enclose the speed increasing/reducing mechanism (4).
Description
Technical field
The present invention relates to a kind of variable ratio steering apparatus, and make the direction of principal axis length miniaturization of variable ratio steering apparatus.
Background technology
Vehicle is provided with variable ratio steering apparatus, is used to make with respect to the ratio of the steering angle of the wheel of the angle of rotation of bearing circle and the moving velocity of vehicle increase and decrease accordingly.
As variable ratio steering apparatus in the past, the known device that 1 record of patent documentation is for example arranged.This device is provided with variable ratio steering apparatus on the following tween drive shaft, and this tween drive shaft is connected with the steering shaft of bearing circle and the pinion shaft of steering hardware.
This variable ratio steering apparatus is gone up to be provided with at the pinion shaft (output shaft) of steering hardware has the retaining ring of internal tooth, in addition, the thin barrel-contoured flexbile gear that will be formed with the elastically deformable of the external tooth that lacks than the number of teeth of above-mentioned internal tooth on outer peripheral face is connected with steering shaft (input shaft), be provided with the cam of elliptical shape in the inside of above-mentioned flexible rack, make this cam rotation by driving motor, thus, make above-mentioned flexible rack and above-mentioned internal gearing in 180 degree two positions at interval, and the position of flexible rack and internal gearing is moved in a circumferential direction with circumferencial direction.When oval-shaped cam is rotated, the tooth of the outer peripheral face of flexible rack is pushed by each internal tooth and the engaging piece that produces moves, by the rotation of cam 1, pinion shaft with respect to steering shaft only rotation relatively be equivalent to the amount of difference of the number of teeth of the internal tooth of the external tooth of steering shaft side and pinion shaft side.Because rotation by cam 1, steering shaft only rotates the amount of number of teeth difference with respect to the opposite sense of the hand of rotation of miniature gears axial cam, so,, can increase and decrease pinion shaft poor with respect to the relative rotation speed of steering shaft by changing the hand of rotation and the rotating speed of cam.That is,, can increase and decrease the rotating speed of pinion shaft with respect to the rotating speed of steering shaft by reversing rotation of motors and rotating speed.
Patent documentation 1: the spy opens the 2000-211541 communique
The variable ratio steering apparatus of patent documentation 1 record, to assist with driving motor and portion of the fast mechanism of increase and decrease and axially be configured in barrel-contoured enclosure interior, described barrel-contoured housing is connected with the fastening axle that constitutes steering shaft, therefore, variable ratio steering apparatus is elongated along the direction of principal axis of steering shaft, the assembleability variation on vehicle.
Summary of the invention
So, the purpose of this invention is to provide a kind of variable ratio steering apparatus that solves above-mentioned problem.
The invention of technical scheme 1 is characterised in that, dispose input shaft that is connected with turning member and the output shaft that is connected with the pinion shaft of steering hardware coaxially, in the relative relative portion in the end of the end of above-mentioned input shaft and above-mentioned output shaft, be provided with the increase and decrease speed mechanism portion of increase and decrease with respect to the rotating speed of the above-mentioned output shaft of above-mentioned input shaft rotational speed, this increases and decreases portion of fast mechanism and has the 1st planetary wheel, the 2nd planetary wheel, columnar portion and rotating cam, above-mentioned the 1st planetary wheel is provided with input gear in the above-mentioned relative portion of above-mentioned input shaft, in addition, above-mentioned relative portion at above-mentioned output shaft is provided with output gear, on the inner peripheral surface of the opposite side of above-mentioned input gear and above-mentioned output gear, be formed with the 1st internal tooth and the 2nd internal tooth, and be formed with the 1st external tooth with above-mentioned the 1st internal gearing, and the quantity of the 1st external tooth is compared few 1 tooth or 2 teeth with the quantity of above-mentioned the 1st internal tooth; Above-mentioned the 2nd planetary wheel and above-mentioned the 1st planetary wheel are integrally formed, be formed with the 2nd external tooth with above-mentioned the 2nd internal gearing, and the quantity of the 2nd external tooth are lacked 1 tooth or 2 teeth than the quantity of above-mentioned the 2nd internal tooth; Above-mentioned columnar portion is formed between above-mentioned the 1st planetary wheel and above-mentioned the 2nd planetary wheel; Above-mentioned rotating cam is configured between above-mentioned the 1st planetary wheel and above-mentioned the 2nd planetary wheel, on accentric position, the center of above-mentioned relatively input gear and above-mentioned output gear, be formed with eccentric orfice with center, be ring-type, to drive the center describe with above-mentioned the 1st internal tooth and above-mentioned the 2nd internal tooth be the circular arc at center by above-mentioned columnar portion being embedded this eccentric orfice and rotation, and above-mentioned the 1st planetary wheel and above-mentioned the 2nd planetary wheel are rotated, the 1st engaging piece of above-mentioned the 1st external tooth and above-mentioned the 1st internal gearing and the 2nd engaging piece of above-mentioned the 2nd external tooth and above-mentioned the 2nd internal gearing are moved to circumferencial direction, control the outside of the motor configurations of portion of the fast mechanism of above-mentioned increase and decrease at the radial direction of portion of the fast mechanism of above-mentioned increase and decrease, be provided with around portion of the fast mechanism of above-mentioned increase and decrease by this electric motor driven barrel-contoured axle drive shaft, above-mentioned rotating cam can one be arranged on the above-mentioned axle drive shaft rotatably, can be set at the 1st reduction ratio between above-mentioned the 1st internal tooth and above-mentioned the 1st external tooth and the value that varies in size of the 2nd reduction ratio between above-mentioned the 2nd internal tooth and above-mentioned the 2nd external tooth.
According to the present invention, when making the rotating cam rotation by electrical motor, by the rotation of this rotating cam, circle and rotation are depicted in the 1st planetary wheel and the 2nd planetary center with columnar portion of the eccentric orfice that embeds rotating cam.Therefore, the 2nd engaging piece of the 2nd internal gearing of the 1st engaging piece of the 1st internal gearing of the 1st planetary the 1st external tooth and input gear and the 2nd planetary the 2nd external tooth and output gear is positioned at the same position of circumferencial direction, under the state that keeps same position, the 1st engaging piece, the 2nd engaging piece move to circumferencial direction.At this moment, the 1st planetary wheel, the 2nd planetary wheel are to the direction opposite with the hand of rotation of rotating cam rotation the 1st planetary wheel, amount that the 2nd planetary number of teeth is few with respect to the number of teeth of input gear, output gear just.Here, because the reduction ratio between the 1st internal tooth and the 1st external tooth is set to different values with the reduction ratio between the 2nd internal tooth and the 2nd external tooth, though so the 1st planetary wheel is different with the 2nd planetary rotation amount, but because the 1st planetary wheel and the 2nd planetary wheel be provided with integratedly, so the 2nd internal tooth rotates the amount of the difference of this rotation amount just with respect to the 1st internal tooth.That is,, can increase and decrease the rotation amount of output gear with respect to input gear by make the rotation amount of positive and negative rotation of rotating cam and increase and decrease rotating cam by electrical motor.
The invention of technical scheme 2 is characterised in that, in technical scheme 1 described variable ratio steering apparatus, above-mentioned rotating cam constitutes to the mechanism of suppressing that mutual opposite sense suppresses by pair of cams with this pair of cams, and the peripheral part separately of above-mentioned pair of cams is connected by recess and the chimeric of protuberance with the interior perimembranous of above-mentioned axle drive shaft.
According to the present invention, with pair of cams under the state that mutual opposite sense suppresses, drive pair of cams by axle drive shaft rotation, therefore, between input gear, output gear and the 1st planetary wheel, the 2nd planetary wheel, do not produce the gap.
The invention of technical scheme 3 is characterised in that, in technical scheme 1 or technical scheme 2 described variable ratio steering apparatus, the lockout mechanism of the rotation that stops above-mentioned axle drive shaft is set.
According to the present invention, when stoping the rotation of axle drive shaft by lockout mechanism, the ratio of the rotating speed of input gear and output gear is roughly 1:1, can obtain the setting of zero equal under the situation with direct connection input shaft and output shaft increase and decrease speed ratio.
Variable ratio steering apparatus according to technical scheme 1, dispose input shaft that is connected with turning member and the output shaft that is connected with the pinion shaft of steering hardware coaxially, in the relative relative portion in the end of the end of above-mentioned input shaft and above-mentioned output shaft, be provided with the increase and decrease speed mechanism portion of increase and decrease with respect to the rotating speed of the above-mentioned output shaft of above-mentioned input shaft rotational speed, the outside of controlling this electrical motor that increases and decreases portion of fast mechanism and being configured in the radial direction of portion of the fast mechanism of increase and decrease by this electric motor driven barrel-contoured axle drive shaft, owing to this axle drive shaft being connected with the rotating cam of portion of the fast mechanism of increase and decrease and can one rotating, so with compare along direction of principal axis configuration electrical motor and the structure in the past that increases and decreases portion of fast mechanism, variable ratio steering apparatus shortens along direction of principal axis, and the assembleability on vehicle improves.
Variable ratio steering apparatus according to technical scheme 2, since with pair of cams under the state that mutual opposite sense suppresses, drive pair of cams by the axle drive shaft rotation, therefore, between input gear, output gear and the 1st planetary wheel, the 2nd planetary wheel, do not produce the gap.
According to the deflection angle of technical scheme 3 than comparable steering hardware, when stoping the rotation of axle drive shaft by lockout mechanism, the revolution ratio of input gear and output gear is fixed to roughly 1:1, can obtain the setting of zero equal under the situation with direct connection input shaft and output shaft increase and decrease speed ratio, so take place under the unusual situation at electrical motor etc., can carry out and common steering operation identical operations, can guarantee safety.
Description of drawings
Fig. 1 is the section drawing (embodiment 1) of variable ratio steering apparatus.
Fig. 2 is partly cut-away's variable ratio steering apparatus and the block diagram (embodiment 1) represented.
Fig. 3 is the exploded perspective view (embodiment 1) of variable ratio steering apparatus.
Fig. 4 is that the E of Fig. 1 is to view (embodiment 1).
Fig. 5 is the block diagram (embodiment 1) that the main portion of partly cut-away's variable ratio steering apparatus is represented.
Fig. 6 (a) be the B-B of Fig. 1 to view, be that the A-A of Fig. 1 is to view (embodiment 1) (b).
Fig. 7 (a) be the C-C of Fig. 1 to view, be that the D-D of Fig. 1 is to view (embodiment 1) (b).
Fig. 8 is that the master of variable ratio steering apparatus looks section drawing (embodiment 2).
Fig. 9 is the side cross-sectional, view (embodiment 2) of variable ratio steering apparatus.
Figure 10 is the exploded perspective view (embodiment 2) of variable ratio steering apparatus.
Label declaration
1... variable ratio steering apparatus
2... input shaft
3... output shaft
4... increase and decrease portion of fast mechanism
5... electrical motor
6... input gear
6a... the 1st internal tooth
7... output gear
7a... the 2nd internal tooth
9... the 1st planetary wheel
9a... the 1st external tooth
10... the 2nd planetary wheel
10a... the 2nd external tooth
11... planetary wheel
11a... columnar portion
12... the 1st cam
13... the 2nd cam
12b, 13b... keyway (recess)
12c, 13c... eccentric orfice
14... rotating cam
15... spring (suppressing mechanism)
16... locking tray (axle drive shaft)
16a... key portion (protuberance)
19,31... screw actuator (lockout mechanism)
A... the 1st engaging piece
B... the 2nd engaging piece
The specific embodiment
Below, the embodiment of variable ratio steering apparatus of the present invention is described.
At first, embodiments of the present invention 1 are described.
Fig. 1 represents the section drawing of variable ratio steering apparatus, and Fig. 2 represents the block diagram that part is cut open, and Fig. 3 represents exploded perspective view.Structure to variable ratio steering apparatus shown in Figure 11 describes below.Dispose input shaft 2 and output shaft 3 coaxially, above-mentioned input shaft 2 is connected with the graphic bearing circle that do not have as turning member, and above-mentioned output shaft 3 is connected with pinion shaft in the steering hardware that is made of rack-and-pinion.In the relative portion relative of the end of above-mentioned input shaft 2, be provided with the increase and decrease speed mechanism portion 4 of increase and decrease with respect to the rotating speed of the output shaft 3 of the rotating speed of input shaft 2 in mode around this relative portion with the end of above-mentioned output shaft 3.And the axle drive shaft 16 of controlling this electrical motor that increases and decreases portion of fast mechanism 45 and driving by this electrical motor 5 is to be arranged on this radial direction that increases and decreases portion of fast mechanism 4 outside around this mode that increases and decreases portion of fast mechanism 4.
Structure to portion of the fast mechanism of above-mentioned increase and decrease 4 describes.Input gear 6 is formed on the above-mentioned relative portion of above-mentioned input shaft 2, on the other hand, output gear 7 is formed on the above-mentioned relative portion of above-mentioned output shaft 3, on the opposite face of input gear 6 and output gear 7, be formed with recess, on the inner peripheral surface of this recess, be formed with the 1st internal tooth 6a and the 2nd internal tooth 7a.And, be provided with housing 8 in the mode that covers input gear 6, output gear 7.Housing 8 is made of housing body 8a that round-ended cylinder shape is roughly arranged and roughly disc shaped lid 8b, and housing 8 combines with car body.Above-mentioned input shaft 2, above-mentioned output shaft 3 can be supported in the housing 8 via pair of bearings 18 with rotating freely, the end face butt of the end face of above-mentioned input gear 6 and above-mentioned output gear 7 and the inner ring of each bearing 18.
Between axial input gear 6 and output gear 7, be provided with as lower member, promptly, be formed with the 1st planetary wheel 9 of the 1st external tooth 9a that is meshed with above-mentioned the 1st internal tooth 6a and be formed with the 2nd planetary wheel 10, the 1 planetary wheels 9 of above-mentioned the 2nd internal tooth 7a ingear the 2nd external tooth 10a and the 2nd planetary wheel 10 integrated and be formed in the planetary wheel 11 that direction of principal axis is grown via the columnar portion 11a that forms with one heart with the 1st planetary wheel 9 and the 2nd planetary wheel 10.This planetary wheel 11 is sandwiched between input gear 6 and the output gear 7 via the little resin packing ring 29 of diameter.The number of teeth of above-mentioned the 1st internal tooth 6a is that the number of teeth of 32, the 1 external tooth 9a is lacked 2 and be 30 by comparison.On the other hand, the number of teeth of above-mentioned the 2nd internal tooth 7a is that the number of teeth of 25, the 2 external tooth 10a is lacked 2 and be 23 by comparison.
As described above planetary wheel 11 is configured between the input gear 6 and output gear 7 on the direction of principal axis, the columnar portion 11a of this planetary wheel 11 is configured to embed the in-to-in state of the rotating cam 14 that the 1st cam 12 and the 2nd cam 13 by ring-type constitute.That is, constitute as follows.By shown in Fig. 7 (b), making this rotating cam 14 rotations like that, rotating cam 14 is with the 1st internal tooth 6a, move for the center makes center " P " rotation of planetary wheel 11 at the center of the 2nd internal tooth 7a " O ", make the 1st external tooth 9a and the 1st internal tooth 6a ingear the 1st engaging piece A of planetary wheel 11 and shown in Fig. 6 (b), make the 2nd external tooth 10a and the 2nd internal tooth 7a ingear the 2nd engaging piece B moves along circumferencial direction, as shown in Figure 3, in the 1st cam 12 and the 2nd cam 13 any one all is to be formed with eccentric orfice 12c on the plectane of the outer peripheral face with circular shape, the structure of 13c, above-mentioned eccentric orfice 12c, 13c is the center with the position of the identical amount of the center off-centre of relative this outer peripheral face.On the mutual relative face of the 1st cam the 12, the 2nd cam 13, be formed with slotted hole 12a, 13a along each circumferencial direction, in the receiving space that forms by this slotted hole 12a, 13a, contain as suppressing the mono-spring 15 of mechanism.The 1st cam the 12, the 2nd cam 13 is sandwiched the peripheral part side between input gear 6 and the output gear 7 via large diameter resin packing ring 28.
The mode of describing circular arc with the center " P " of planetary wheel 11 is rotated driving to this planetary wheel 11, therefore, in order to make the 1st cam 12 and the rotation of the 2nd cam 13, contains above-mentioned electrical motor 5 in the in-to-in peripheral part side of housing 8.Electrical motor 5 is made of circular stator 5b, coil 5a and circular rotor 5c.And, be pressed into the chimeric barrel-contoured locking tray 16 that has as axle drive shaft in the inboard of rotor 5c.This locking tray 16 via the pair of bearings 17 at the both ends of the side that sets within it, can be supported on rotatably in the housing 8.On the axial midway location of the inner peripheral surface of locking tray 16, form the 16a of key portion as side-prominent protuberance in radial direction, on the other hand, on the outer peripheral face of the 1st cam 12 that constitutes above-mentioned rotating cam 14 and the 2nd cam 13, be formed with keyway 12b, 13b as recess, as shown in Figure 5, the above-mentioned key 16a of portion arranged in that this keyway 12b, 13b internal clearance are chimeric.As Fig. 6, shown in Figure 7, it is bigger than the width dimensions of the 16a of key portion that the circumferencial direction of keyway 12b, 13b microscler becomes.Because the effect by spring 15 and with the 1st cam 12, the 2nd cam 13 suppresses and departs from the phase angle of the mutual angulation of conduct to the direction of mutually reciprocal rotation, increase the offset of rotating cam 14, so this rotating cam 14 is pushed to the 1st internal tooth 6a and the 2nd internal tooth 7a, and the gap of the 1st engaging piece A and the 2nd engaging piece B disappears, on the other hand, when making electrical motor 15 rotations and making locking tray 16 rotations, the strong 16a of portion pushes the keyway 12b of the 1st cam 12 and the 2nd cam 13, the end face of the side of 13b, thus, the keyway 12b of the 1st cam 12 and the 2nd cam 13, the position of 13b is moved also overlapping to the direction of unanimity, thus, the offset of rotating cam 14 reduces and produce the gap on the 1st engaging piece A and the 2nd engaging piece B, successfully carries out moving of the 1st engaging piece A and the 2nd engaging piece B.In order successfully to bring into play such effect, between the inner peripheral surface of the outer peripheral face of the 1st cam the 12, the 2nd cam 13 and locking tray 16, form the gap of departing from the phase angle that can produce the 1st cam 12 and the 2nd cam 13.
With the number of teeth of the 1st internal tooth 6a that constitutes the 1st engaging piece A is that the number of teeth of the 32 and the 1st external tooth 9a is 30 relative, the number of teeth that constitutes the 2nd internal tooth 7a of the 2nd engaging piece B is that the number of teeth of the 25 and the 2nd external tooth 10a is 23, owing to compare with the gear that constitutes the 1st engaging piece A, the number of teeth of gear that constitutes the 2nd engaging piece B is few, so with the 1st reduction ratio G1 between the 1st internal tooth 6a and the 1st external tooth 9a is that 32/ (32-30)=16 are relative, the 2nd reduction ratio G2 between the 2nd internal tooth 7a and the 2nd external tooth 10a is 25/ (25-23)=12.5, and is set at different values.
Do not rotate with respect to the locking tray 16 of the rotating speed of the output shaft 3 of the rotating speed of input shaft 2 in order to be used in increase and decrease, be provided with lockout mechanism.As shown in Figure 4, be housed in the inside of housing 8 as the screw actuator 19 of lockout mechanism and dispose with meeting at right angles with input shaft 2, output shaft 3.Spring 19b that screw actuator 19 has bar 19a, suppress to the direction of pulling out this bar 19a and the elastic force pressure of resisting this spring 19b and coil 19c that bar 19a is drawn in.In the inside of housing 8, securing rod 20 is via being supported freely to rotate that with lid 8b all-in-one-piece axial region 8c an end of securing rod 20 can be connected with the front end of bar 19a freely to rotate via pin 19d.The other end of this securing rod 20 is along the radial direction bending of locking tray 16, by the rotation of securing rod 20 restriction locking trays 16, so, equally spaced form a plurality of lock slots 16b in the end of locking tray 16 along circumferencial direction.
As shown in Figure 1, at above-mentioned input gear 6 and central parts above-mentioned output gear 7 opposing end faces, form towards the outstanding urceolus 2a of above-mentioned output gear 7, the in-to-in inner core 3a that inserts logical this urceolus 2a is integrally formed in the end face of above-mentioned output gear 7.And, inside at this inner core 3a, be provided with spring 21 and slide unit 22, this spring 21 is as above-mentioned input gear 6 and above-mentioned output gear 7 are suppressed mechanism to what the direction that deviates from was mutually suppressed, one end of above-mentioned slide unit 22 suppresses by above-mentioned spring 21, and the other end contacts with the shaft core position point of the end face of above-mentioned input shaft 2.The leading section of this slide unit 22 forms dome shape because contact with the end face point of input gear 6, forms minor diameter part 22a at base end part.And this minor diameter part 22a embeds the inside of spring 21.And, between urceolus 2a and inner core 3a, be provided with barrel-contoured needle bearing 23.
Next, the effect to variable ratio steering apparatus 1 describes.
When making when not having the rotation of graphic bearing circle input shaft 2 rotations.At this moment, if driving motor 5 not, then since rotating cam 14 do not rotate, so the center of planetary wheel 11 " P " do not move.Therefore, by the rotation of input gear 6, planetary wheel 11 does not revolve round the sun (rotation) and rotation, similarly, by the rotation of planetary wheel 11, output gear 7 rotations.That is, the rotation of input shaft 2 is delivered to output shaft 3 with maintaining the original state.On the other hand, if this moment to electrical motor 5 energising and make rotor 5c and locking tray 16 rotations, then since the 16a of the key portion movable fit of this locking tray 16 in keyway 12b, 13b, so the 1st cam 12 and 13 rotations of the 2nd cam.Owing to form the center " P " of eccentric orfice 12c, 13c of the inner peripheral surface of the rotating cam 14 that constitutes by the 1st cam 12 and the 2nd cam 13, center " O " off-centre with respect to the circular arc of the outer peripheral face that forms rotating cam 14, so when rotating cam 14 rotations, engaging piece A, B that the 1st planetary wheel the 9, the 2nd planetary wheel 10 of formation planetary wheel 11 forms with the 2nd internal tooth 7a engagement of the 1st internal tooth 6a of input gear 6 and output gear 7 move to circumferencial direction.
The state that Fig. 6 (a) and (b) and Fig. 7 (a) and (b) are expressed as follows, promptly, the center of planetary wheel 11 " P " is eccentric upward with respect to the internal diameter center " O " of the 2nd internal tooth 7a of the 1st internal tooth 6a of input gear 6 and output gear 7, thus, the 1st planetary wheel the 9, the 2nd planetary wheel 10 moves to the top of the 1st internal tooth 6a, the 2nd internal tooth 7a, in engaging piece A, the engagement of B place.The 2nd engaging piece B shown in the 1st engaging piece A shown in Fig. 7 (b) and Fig. 6 (b) occupies the same position of circumferencial direction, by planetary wheel 11 from this position to right-hand revolution, the 1st engaging piece A, the 2nd engaging piece B are to one week of right-hand revolution.At this moment, the 1st planetary wheel 9 and the 2nd planetary wheel 10 only rotate following amount to the anticlockwise direction opposite with the hand of rotation of planetary wheel 11, that is, the number of teeth of the 1st planetary wheel 9 and the 2nd planetary wheel 10 is with respect to the few amount of the number of teeth of input gear 6, output gear 7.If change view, conversely, input gear 6 is with respect to the revolution of the 1st planetary wheel 9, only to the many amounts of the right-hand revolution number of teeth identical with the hand of rotation of planetary wheel 11, simultaneously, with respect to the 2nd planetary wheel 10, output gear 7 is only to the many amounts of the right-hand revolution number of teeth identical with the hand of rotation of planetary wheel 11.Promptly, make the reduction ratio G1 between the 1st internal tooth 6a and the 1st external tooth 9a be " 16 ", reduction ratio G2 between the 2nd internal tooth 7a and the 2nd external tooth 10a is set at " 12.5 ", therefore, when making planetary wheel 11 to right-hand revolution 1 during week, input gear 6 is to right-hand revolution α=(1/16), and output gear 7 is also to right-hand revolution β=(1/12.5).Here, because input gear 6 is different with the rotation amount of output gear 7, so the difference of this rotation amount becomes the relative rotation amount of output gear 7 with respect to input gear 6.
Below be specifically described, in Fig. 7 (b), at planetary wheel 11 to right-hand revolution 1 during week, occupy (R) point of the 1st planetary wheel 9 of the same position of circumferencial direction with (Q) of input gear 6 point, the number of teeth that moves the 1st planetary wheel 9 to anticlockwise direction just is with respect to the amount (32-30=2) of 2 teeth of input gear 6 deficiencies and (R ') after moving to rotation " α " position of putting.At this moment, shown in Fig. 6 (b), (T) point that occupies the position identical with (S) point of output gear 7 is present on the 2nd planetary wheel 10, (S) point of described output gear 7 is corresponding with (Q) point of Fig. 7 (b) in a circumferential direction, when planetary wheel 11 to right-hand revolution 1 during week, should (T) point just the number of teeth of rotation the 2nd planetary wheel 10 with respect to the amount (25-23=2) of 2 teeth of output gear 7 deficiencies and occupy the position of (T ') point after anticlockwise direction rotation " β ".Here, because the 1st planetary wheel 9 and the 2nd planetary wheel 10 are by integrated and formation planetary wheel 11, so (R ') point and (T ') point are the same point on the planetary wheel 11.Therefore, as mentioned above, input gear 6 rotates " α " with respect to planetary wheel 11 just to clockwise direction, it is equal just rotating " β " with respect to planetary wheel 11 to clockwise direction with output gear 7, and input gear 6 rotates " α " just, can replace to output gear 7 and rotate " β " just to clockwise direction to clockwise direction.
Because " β-α "=(1/12.5)-(1/16) ≈ (1/57), so when planetary wheel 11 with respect to input gear 6 and output gear 7 to right-hand revolution during 1 week, output gear 7 relatively only rotates (1/57) week to clockwise direction with respect to input gear 6.
That is, the rotating speed of output gear 7 increases with respect to the rotating speed of input gear 6.And recruitment changes by the rotating speed of increase and decrease electrical motor 5.If with the hand of rotation of electrical motor 5 conversely, then the rotating speed of output gear 7 reduces with respect to the rotating speed of input gear 6, and reduction changes by the rotating speed of increase and decrease electrical motor 5.
On the other hand, by applying external force on the tire conversely when output shaft 3 sideway swivels drive output gear 7, though output gear 7 will rotate and drive inboard planetary wheel 11 in Fig. 6 (b), but because the relation of the cam angle of inertia, reduction ratio and the rotating cam 14 of electrical motor 5, can't be via planetary wheel 11 reverse drive rotating cam 11.And, because the rigidity of tooth is big, so can climbing tooth (Dentistry do not jump び).That is, rotational force can not be delivered to a pair of the 1st cam 12 and the 2nd cam 13, and electrical motor 5 can be from external drive.
Stopping owing to driving engine or the fault of electric system causes under the electrical motor 5 non-rotary situations, stopping to screw actuator 19 energisings.Therefore, bar 19a gives prominence to by the elastic force pressure of spring 19b, and the leading section of securing rod 20 enters the lock slots 16b of locking tray 16.In view of the above, the rotor 5 of electrical motor 5 is locked, and the rotation of input gear 6 is delivered to output gear 7 with maintaining the original state via planetary wheel 11.Therefore, input gear 6 and output gear 7 rotate to same direction with the ratio that revolution ratio is roughly 1:1 (being 1:0.98 in the present embodiment).
According to the present invention, by spring 15 with the 1st cam 12 and the 2nd cam 13 under the state that mutually opposite direction is suppressed, owing to drive the 1st cam 12 and the 2nd cam 13 by locking tray 16 rotations, so, between input gear 6, output gear 7 and the 1st planetary wheel the 9, the 2nd planetary wheel 10, do not produce the gap.
According to the present invention, when stoping the rotation of locking trays 16 by screw actuator 19, the revolution ratio of input gear 6 and output gear 7 is 1:1, obtains the setting of zero equal under the situation with direct connection input shaft 6 and output shaft 7 increase and decrease speed ratio.
(b) embodiment 2
Next, embodiment 2 is described.
As Fig. 8, shown in Figure 9, in the present embodiment, dispose electrical motor 24 with input shaft 2, output shaft 3 in the radial direction outside of portion of the fast mechanism of increase and decrease 4 with meeting at right angles.That is, constitute as follows.As shown in figure 10, housing 8d and housing 8a form.And as shown in Figure 9, electrical motor 24 combines with housing 8d via bolt 30, and worm shaft 27 can be supported in the inside of housing 8d with rotating freely via bearing 25,26.One end of this worm shaft 27 is pressed on the output shaft 24a that is combined in electrical motor 24.And, in embodiment 1, being formed with worm gear 16c on the outer peripheral face as the above-mentioned locking tray 16 of axle drive shaft of explanation, the worm screw 27a of above-mentioned worm shaft 27 and this worm gear 16c mesh.
The lockplate 24b that is formed with a plurality of lock slots on outer peripheral face combines with the output shaft 24a of above-mentioned electrical motor 24.On the other hand, as shown in Figure 8, on housing 8d, be formed with recess 8e, contain screw actuator 31 among this recess 8e and constitute lockout mechanism, above-mentioned helical bar 31 make bar and worm shaft 27 axis parallel give prominence to and be entrenched in the above-mentioned lock slots of above-mentioned lockplate 24b.In above-mentioned recess 8e, the lid 33 of closing above-mentioned recess 8e is installed via spring 32.This screw actuator 31 is also identical with above-mentioned screw actuator 19, when energising, resist the inside that does not have the elastic force pressure of graphic spring and bar is introduced coil, under the state that does not have energising, bar is given prominence to and is entered by the elastic force pressure that does not have graphic spring in the lock slots of lockplate 24b, with locking tray 16 lockings.Therefore, in embodiment 2, shown in the exploded perspective view of Figure 10, omit the locking ditch 16b of screw actuator 19 grades and locking tray 16.
Effect to this variable ratio steering apparatus describes below.In the present embodiment, the rotation of the output shaft 24a of electrical motor 24 is delivered to worm shaft 27, and the rotation of this worm shaft 27 is delivered to locking tray 16 via worm screw 27a and worm gear 16c.On the other hand, under situation with locking tray 16 lockings, the energising of removed from solenoid 31, the lock slots of lockplate 24b given prominence to and enters by bar by the elastic force pressure that does not have graphic spring.
Because other structure, effect are identical with embodiment 1, therefore omit explanation.
In addition, in embodiment 1,2,, also can use 1 rotating cam identical with the 1st cam or the 2nd cam face though rotating cam is made of the 1st cam, the 2nd cam and spring.And, in embodiment 1,2,, also can make G1 conversely less than G2 though make the 1st reduction ratio G1 between the 1st internal tooth and the 1st external tooth greater than the 2nd reduction ratio G2 between the 2nd internal tooth and the 2nd external tooth.
Claims (11)
1. variable ratio steering apparatus, the vehicle that is used to comprise bearing circle He has the steering hardware of pinion shaft, this variable ratio steering apparatus comprises:
Be used to be connected in the input shaft (2) of bearing circle,
With the output shaft (3) that input shaft disposes coaxially, this output shaft (3) is connected in the pinion shaft of steering hardware,
Be used for the increase and decrease speed mechanism portion (4) of change with respect to the rotating speed of the output shaft (3) of the rotating speed of input shaft (2), this increases and decreases portion of fast mechanism and is arranged between the axial end portion of the axial end portion of input shaft respect to one another (2) on the direction of principal axis of input shaft and output shaft and output shaft (3), and this increases and decreases portion of fast mechanism and comprises:
Input gear (6), this input gear are arranged on the axial end portion of input shaft (2) and are formed with the 1st internal tooth (6a) on the inner peripheral surfaces of input gear,
Output gear (7), this output gear is arranged on the axial end portion of output shaft (3), and is formed with the 2nd internal tooth (7a) on the inner peripheral surface of output gear, and output gear and input gear have common centre of gration (O),
The 1st planetary wheel (9), the 1st planetary wheel is formed with the 1st external tooth (9a), and the 1st external tooth and the 1st internal tooth (6a) mesh and form the 1st engaging piece (A), and the number of teeth of ratio of number of teeth the 1st internal tooth (6a) of the 1st external tooth (9a) is few, between the 1st external tooth and the 1st internal tooth, provide the 1st reduction ratio thus
The 2nd planetary wheel (10), the 2nd planetary wheel is formed with the 2nd external tooth (10a), the 2nd external tooth and the 2nd internal tooth (7a) engagement and form the 2nd engaging piece (B), the number of teeth of ratio of number of teeth the 2nd internal tooth (7a) of the 2nd external tooth (10a) is few, between the 2nd external tooth and the 2nd internal tooth, provide second reduction ratio thus, the 2nd reduction ratio is arranged to the value different with the 1st reduction ratio
Columnar portion (11a), the 1st planetary wheel (9) and the 2nd planetary wheel (10) are integrally joined to each other by this columnar portion (11a), and,
Rotating cam (14), this rotating cam is arranged between the 1st planetary wheel (9) and the 2nd planetary wheel (10), and be formed with the eccentric orfice that has with respect to common centre of gration (O) the accentric center of above-mentioned input gear (6) and above-mentioned output gear (7), above-mentioned columnar portion (11a) embeds rotating cam (14) by eccentric orfice
Electrical motor (5,24), this electrical motor are arranged on the radial outside of increase and decrease portion of fast mechanism (4), and portion of the fast mechanism of control increase and decrease, and
By the axle drive shaft (16) that electrical motor (5) rotation drives, this axle drive shaft forms hollow tube-shape and centers on increase and decrease portion of fast mechanism (4),
Wherein, utilize electrical motor (5) by axle drive shaft (16) rotation driven in rotation cam (14), thereby the 1st planetary wheel (9) and the 2nd planetary wheel (10) are rotated around the common centre of gration (O) of input gear and output gear, therefore, allow the 1st engaging piece (A) and the 2nd engaging piece (B) on the 1st planetary wheel and the 2nd planetary circumferencial direction, to move.
2. variable ratio steering apparatus as claimed in claim 1, it is characterized in that, rotating cam (14) comprises pair of cams (12,13) and suppresses mechanism (15) to opposite this pair of cams of hand of rotation bias voltage, above-mentioned pair of cams and above-mentioned axle drive shaft (16) interconnect by the chimeric of recess and protuberance, one of recess and protuberance are formed on each the outer peripheral face of pair of cams (12,13), and another of recess and protuberance is formed on the inner peripheral surface of axle drive shaft (16).
3. variable ratio steering apparatus as claimed in claim 1 or 2 is characterized in that, further comprises the lockout mechanism of the spinning movement that stops above-mentioned axle drive shaft (16).
4. variable ratio steering apparatus as claimed in claim 1 or 2 is characterized in that, few 1 or 2 of the number of teeth of ratio of number of teeth the 1st internal tooth (6a) of the 1st external tooth (9a), and the number of teeth of ratio of number of teeth the 2nd internal tooth (7a) of the 2nd external tooth (10a) is lacked 1 or 2.
5. variable ratio steering apparatus as claimed in claim 1 or 2 is characterized in that, it is parallel with output shaft (3) with input shaft (2) that electrical motor (5) is configured to its S. A..
6. variable ratio steering apparatus as claimed in claim 5 is characterized in that, axle drive shaft (16) fits into electrical motor (5) and directly upwards is arranged between electrical motor and the increase and decrease portion of fast mechanism (4) at it.
7. variable ratio steering apparatus as claimed in claim 1 or 2 is characterized in that, it is vertical with output shaft (3) with input shaft (2) that electrical motor (24) is configured to its S. A..
8. variable ratio steering apparatus as claimed in claim 2, it is characterized in that, each of pair of cams (12,13) all has recess (12b, 13b), and axle drive shaft (16) has protuberance (16a), this recess and protuberance extend on the circumferencial direction of cam (12,13) and axle drive shaft (16), and the length of recess is bigger than the length of protuberance, protuberance (16a) thus in recess, move in a circle the recess of pair of cams (12,13) aligned each other.
9. variable ratio steering apparatus as claimed in claim 3, it is characterized in that, lockout mechanism comprises screw actuator (19) and latch recess (16b), and this latch recess is formed on axle drive shaft (16) and goes up also and can engage with the parts (20) of screw actuator control on the circumferencial direction of axle drive shaft (16).
10. variable ratio steering apparatus as claimed in claim 3, it is characterized in that, lockout mechanism comprises screw actuator (31) and lockplate (24b), and this lockplate is arranged on electrical motor (24) and goes up and be formed with a plurality of lock slots, this lock slots can with the part bonding of screw actuator control.
11. variable ratio steering apparatus as claimed in claim 3 is characterized in that, axle drive shaft (16) comprises worm gear (16c), and this worm gear is formed on the outer peripheral face of axle drive shaft, and electrical motor (24) comprises the worm gear engaged worm axle (27) with axle drive shaft.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007310060A JP2009132269A (en) | 2007-11-30 | 2007-11-30 | Variable ratio steering device |
| JP2007310060 | 2007-11-30 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101445127A true CN101445127A (en) | 2009-06-03 |
Family
ID=40239637
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2008101797307A Pending CN101445127A (en) | 2007-11-30 | 2008-11-28 | Variable ratio steering apparatus |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20090139356A1 (en) |
| EP (1) | EP2065292A2 (en) |
| JP (1) | JP2009132269A (en) |
| KR (1) | KR20090056897A (en) |
| CN (1) | CN101445127A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107228164A (en) * | 2017-07-13 | 2017-10-03 | 中冶赛迪技术研究中心有限公司 | The periodically variable planet-gear transmission device of gearratio |
| CN107310621A (en) * | 2016-04-27 | 2017-11-03 | 长城汽车股份有限公司 | For the variable ratio steering gear of vehicle and the vehicle with it |
| CN112744287A (en) * | 2019-10-31 | 2021-05-04 | 操纵技术Ip控股公司 | Handwheel actuator of steer-by-wire system |
| CN114159856A (en) * | 2021-10-27 | 2022-03-11 | 湖南正信检测技术股份有限公司 | Filtering device for food detection |
| CN114270074A (en) * | 2019-09-05 | 2022-04-01 | 池田昌幸 | Gear speed change device |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE534469C2 (en) * | 2010-01-11 | 2011-09-06 | Scania Cv Ab | Device for active steering of a truck and steering device with such device |
| DE102012219548A1 (en) * | 2012-07-18 | 2014-01-23 | Takata AG | Locking device for locking a movable component |
| JP6599220B2 (en) * | 2015-12-01 | 2019-10-30 | 日本電産シンポ株式会社 | Reducer with electric motor |
| US9911754B1 (en) * | 2016-10-07 | 2018-03-06 | Macronix International Co., Ltd. | 3D memory structure |
| US11498616B2 (en) * | 2019-03-07 | 2022-11-15 | Trw Automotive U.S. Llc | Apparatus for use in turning steerable vehicle wheels |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4520693A (en) * | 1981-10-07 | 1985-06-04 | Sfredda Albert P | High ratio drive |
| US5102377A (en) * | 1991-04-08 | 1992-04-07 | Stanley Spanski | Rotary actuator with epicyclic transmission |
| JP3536296B2 (en) | 1999-01-22 | 2004-06-07 | トヨタ自動車株式会社 | Vehicle steering control device |
| JP4388383B2 (en) * | 2004-01-07 | 2009-12-24 | 本田技研工業株式会社 | Vehicle steering system |
| EP1857347B1 (en) * | 2006-05-15 | 2009-08-19 | JTEKT Corporation | Steering apparatus for vehicle |
| JP2007310060A (en) | 2006-05-17 | 2007-11-29 | Fujifilm Corp | Photosensitive resin composition and photosensitive film, permanent pattern forming method, and printed wiring board |
| JP5013193B2 (en) * | 2007-10-22 | 2012-08-29 | 株式会社ジェイテクト | Vehicle steering system |
-
2007
- 2007-11-30 JP JP2007310060A patent/JP2009132269A/en active Pending
-
2008
- 2008-11-10 EP EP08019630A patent/EP2065292A2/en not_active Withdrawn
- 2008-11-18 US US12/272,833 patent/US20090139356A1/en not_active Abandoned
- 2008-11-28 CN CNA2008101797307A patent/CN101445127A/en active Pending
- 2008-11-28 KR KR1020080119569A patent/KR20090056897A/en not_active Application Discontinuation
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107310621A (en) * | 2016-04-27 | 2017-11-03 | 长城汽车股份有限公司 | For the variable ratio steering gear of vehicle and the vehicle with it |
| CN107228164A (en) * | 2017-07-13 | 2017-10-03 | 中冶赛迪技术研究中心有限公司 | The periodically variable planet-gear transmission device of gearratio |
| CN107228164B (en) * | 2017-07-13 | 2023-04-14 | 中冶赛迪技术研究中心有限公司 | Small tooth difference planetary gear transmission device with periodically changed transmission ratio |
| CN114270074A (en) * | 2019-09-05 | 2022-04-01 | 池田昌幸 | Gear speed change device |
| CN114270074B (en) * | 2019-09-05 | 2024-02-20 | 池田昌幸 | Gear speed variator |
| CN112744287A (en) * | 2019-10-31 | 2021-05-04 | 操纵技术Ip控股公司 | Handwheel actuator of steer-by-wire system |
| US11745789B2 (en) | 2019-10-31 | 2023-09-05 | Steering Solutions Ip Holding Corporation | Handwheel actuator for steer by wire system |
| CN114159856A (en) * | 2021-10-27 | 2022-03-11 | 湖南正信检测技术股份有限公司 | Filtering device for food detection |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2065292A2 (en) | 2009-06-03 |
| US20090139356A1 (en) | 2009-06-04 |
| KR20090056897A (en) | 2009-06-03 |
| JP2009132269A (en) | 2009-06-18 |
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Open date: 20090603 |